Tire inflation system

ABSTRACT

A tire inflation system and method for a tire supported by a wheel, the tire inflation system including a pump system including a pump cavity configured to fluidly connect to the tire, an actuating element configured to actuate relative the pump cavity, a drive mechanism rotatably coupled to the wheel, the drive mechanism including a motion transformer and an eccentric mass, a valve fluidly connecting the pump cavity to a fluid reservoir; and a control system configured to operate the valve.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. application Ser. No.15/280,737 filed 29 Sep. 2016, which is a continuation-in-part of U.S.application Ser. No. 14/839,009 filed 28 Aug. 2015, which is acontinuation of U.S. application Ser. No. 14/198,967 filed 6 Mar. 2014,which is a continuation of U.S. application Ser. No. 14/019,941 filed 6Sep. 2013, which is a continuation of U.S. application Ser. No.13/797,826 filed 12 Mar. 2013, all of which are incorporated in theirentireties by this reference. This application claims the benefit ofU.S. Provisional Application No. 62/235,121 filed 30 Sep. 2015, which isincorporated in its entirety by this reference.

TECHNICAL FIELD

This invention relates generally to the pumping field, and morespecifically to a new and useful tire inflation system in the pumpingfield.

BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is a schematic representation of the tire inflation systemcoupled to a rotating surface.

FIGS. 2A-2C are schematic representations of variations of the pumpsystem and the stabilization mechanism.

FIGS. 3A-3B are perspective views of variations of the processing systemand sensor set of the tire inflation system.

FIG. 4 is a schematic representation of the tire inflation system.

FIG. 5 is a schematic representation of the tire inflation system.

FIG. 6 is a schematic representation of the tire inflation system.

FIG. 7 is a schematic representation of the tire inflation system.

FIGS. 8A, 8B, and 8C are cutaway views of a variation of the tireinflation system in the recovery stroke, at the beginning of thecompression stroke, and at the end of the compression stroke,respectively.

FIG. 9 is a flow chart representation of a method for inflating a tiresupported by a wheel.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The following description of the preferred embodiments of the inventionis not intended to limit the invention to these preferred embodiments,but rather to enable any person skilled in the art to make and use thisinvention.

1. Overview

As shown in FIG. 1, a tire inflation system for a tire supported by awheel includes: a pump system including a pump cavity configured tofluidly connect to the tire, an actuating element configured to actuaterelative the pump cavity, a drive mechanism rotatably coupled to thewheel, the drive mechanism including a motion transformer and aneccentric mass, a valve fluidly connecting the pump cavity to a fluidreservoir, and a control system communicably coupled to the valve, andconfigured to operate the valve.

The tire inflation system functions to convert rotary motion (e.g., of atire) into a pumping force. In one application, the inflation system canconvert rotation of a rotating surface (e.g., a tire) into radialpumping force via relative motion between an eccentric mass (e.g.,offset mass) and the rotating surface. The inflation systems and methodscan additionally or alternatively automatically detect and mitigateeccentric mass spin, which can result from rotating surface rotation ator near a resonant frequency of the eccentric mass.

2. Benefits

The system and/or method can confer several benefits over conventionalmethodologies used for inflating tires. For example, conventionalmethodologies (e.g., manual tire inflation) can be expensive andinconvenient. In specific examples, the system and/or method can conferone or more of the following:

First, the technology can optimize the pressurization of tires.Underinflated tires can contribute to low fuel efficiency and otherissues, which are particularly pronounced in the trucking industry,where long distances and large loads amplify the effects of anunderinflated tire. In one application, the inflation technology canautomatically pressurize tires through converting the rotation of arotating surface (e.g., a tire) into radial pumping force via relativemotion between an eccentric mass (e.g., offset mass) and the rotatingsurface.

Second, the technology can overcome issues arising from using therelative motion between an eccentric mass and a rotating surface to pumpa tire. For example, the inflation technology can leverage stabilizationmechanisms (e.g., fluid valves, clutches, eccentric mass-splitting,etc.) to compensate for back forces applied by the pump on the hangingeccentric mass (e.g., during a pump's recover stroke). Such back forcescan disrupt the system in a manner that can adversely affect pumpingpower (e.g., exciting the eccentric mass in a manner that causes it tospin in a mass spin state). In examples with a reciprocating pump, thereciprocating pump can produce a back-torque during the compressionstroke that can contribute to the eccentric mass approaching a mass spinstate. Further, the reciprocating pump can produce an oscillation duringpumping, which can excite the eccentric mass into a mass spin state(e.g., if the frequency of the oscillation is near thegravitationally-induced resonant frequency of the eccentric mass). Thesepotential adverse effects can be particularly pronounced when the pumpsystem rotates at or near the resonant frequency of the drive mechanism.

Third, the technology can actively actuate the stabilization mechanismswith precise timing and execution in order to minimize disruption of thetire pressurization by a mass spin state. The technology can leverage acontrol system (e.g., sensor set, processing system, power module,communications module, etc.) to measure parameters indicative of an massspin state (e.g., using sensors), determine a mass spin state and/orstate preceding an eccentric mass state (e.g., by processing the sensordata with the processing system), and alleviate the mass spin state(e.g., by actively actuating a stabilization mechanism into analleviation mode). Further, in response to alleviation of the mass spinstate, the technology can effectively transition the tire inflationsystem back into a normal tire inflating state (e.g., by activelyactuating a stabilization mechanism into a recovery mode).

The technology can, however, provide any other suitable benefits in thecontext of automatic tire inflation.

3. System

As shown in FIG. 1, a tire inflation system 10 for a tire supported by awheel includes: a pump system 15 including a pump cavity 210 configuredto fluidly connect to the tire, an actuating element 220 configured toactuate relative the pump cavity 210, a drive mechanism rotatablycoupled to the wheel, the drive mechanism including a motion transformer120 and an eccentric mass 140, a valve fluidly connecting the pumpcavity 210 to a fluid reservoir, and a control system 300 electricallyconnected to the valve, and configured to operate the valve. The tireinflation system 10 can additionally or alternatively include a housing30 mountable to a surface of the wheel, a relief valve 135, and/or othersuitable components.

3.1. Pump System

As shown in FIG. 1, the pump system 15 includes a primary pump 200including a pump cavity 210, an actuating element 220, and a pump body240; a drive mechanism 100 configured to drive the primary pump, thedrive mechanism 100 optionally including a motion transformer 120 and aneccentric mass 140, and a drive mechanism couple coupling the drivemechanism 100 to the primary pump 200. The pump system 15 can optionallyinclude a secondary pump 200 b (e.g., substantially similar andmechanically connected to the primary pump, substantially different fromthe primary pump, etc.) and/or any number of pumps. The pump system 15functions to translate rotational motion into a pumping force. In anembodiment, the pump system 15 is configured to translate relativemotion between the primary pump 200 and the motion transformer 120 intoa pumping force, where the eccentric mass 140 retains the motiontransformer position relative to a gravity vector while the primary pump200 rotates relative to the motion transformer 120 (e.g., with arotating surface 20).

The pump system 15 is preferably couplable to a surface that rotatesrelative to a gravity vector, such as a rotating surface 20. Therotating surface 20 is preferably a wheel of a vehicle (e.g., a truck)but can alternatively be any suitable rotating system, such as awindmill, waterwheel, and/or any other suitable rotating surface 20.

The pump system 15 preferably receives fluid from a first reservoir 400and pumps the fluid into a second reservoir 500. The fluid is preferablya gas (e.g., ambient air) but can alternatively be any suitable gas, aliquid, and/or any other suitable fluid. The first reservoir 400 ispreferably the ambient environment, but can alternatively be a fluidsource (e.g., a fluid canister), an intermediary reservoir, and/or anyother suitable reservoir. The second reservoir 500 is preferably a tireinterior, but can alternatively be any suitable reservoir. The pumpsystem 15 can additionally or alternatively treat (e.g., filter) thepumped fluid within a suitable reservoir (e.g., intermediary reservoir)to remove debris, water, and/or or any other suitable undesiredcomponent of the fluid.

However, the pump system 15 can be configured in any suitable manner.

3.1.A. Primary Pump.

The primary pump 200 of the pump system 15 functions to pump fluid intothe reservoir (e.g., a second reservoir 500), thereby pressurizing thereservoir. The primary pump 200 can include a pump cavity 210, anactuating element 220, and/or a pump body 240.

The primary pump 200 is preferably rotatably coupled to the rotationalaxis of the drive mechanism 100. The primary pump 200 is preferablypositioned a radial distance away from the rotational axis of the drivemechanism 100, where the radial position of the primary pump 200 ispreferably fixed, but can alternatively be adjustable. The primary pump200 can be statically mounted to a housing 30 (where the housing 30 isstatically coupled to the rotating surface 20) but can alternatively betransiently mounted to the housing 30 (adjustably mounted).

The primary pump 200 is preferably a positive displacement pump. In thisembodiment, the actuating element 220 preferably forms a substantiallyfluid impermeable seal with the pump cavity 210, within which theactuating element 220 translates to create pressure differentials thatmove a fluid from the pump inlet to the pump outlet of the pump cavity210. Positive displacement pumps can include any one or more of: areciprocating pump (e.g., reciprocating piston pump), peristaltic pump,rotary pump, gear pump screw pump, progressing cavity pump, and/or anyother suitable positive displacement pump. However, the primary pump 200can be an impulse pump, velocity pump, gravity pump, steam pump,valveless pump, in-tire pump, and/or any other suitable pump type.

In a variation where the primary pump is a reciprocating pump, the pumpcavity 210 is preferably a pump chamber and the actuating element 220 ispreferably a reciprocating element. The reciprocating element can be adiaphragm, a piston, a diaphragm actuated by a piston (e.g., where thediaphragm defines the lumen and the piston receives the pumping forcefrom the diaphragm to actuate the diaphragm, etc.), or any othersuitable reciprocating element. The reciprocating pump preferablydefines an actuation axis along which the reciprocating element travelsduring the compression stroke and/or the return stroke. The actuationaxis is preferably substantially normal to the rotational axis, but canbe at any suitable angle to the rotational axis. Additionally oralternatively, the reciprocating pump and/or other types of primarypumps 120 can include elements analogous to embodiments, variations, andexamples described in Ser. No. 14/839,009 filed 28 Aug. 2015, which isherein incorporated in its entirety by this reference.

In a variation where the primary pump is a peristaltic pump, the pumpcavity 210 is preferably a groove (e.g., circumferential groove) and theactuating element 220 is preferably a diaphragm or tube. Additionally oralternatively, the peristaltic pump and/or other types of primary pumps120 can include elements analogous to embodiments, variations, andexamples described in U.S. application Ser. No. 14/199,048 filed on 6Mar. 2014, which is herein incorporated in its entirety by thisreference.

However, the primary pump 200 can be otherwise configured.

3.1.A.i Pump Cavity.

The primary pump 200 can include a pump cavity 210 configured to fluidlyconnect to the rotating surface 20 (e.g., tire). The pump cavity 210functions to facilitate fluid ingress (e.g., from the first reservoir)and/or fluid egress (e.g., into the second reservoir). The primary pump200 can include any number of pump cavities (e.g., substantiallydifferent pump cavities, substantially similar, etc.).

A pump cavity 210 preferably defines at least one inlet and at least oneoutlet. Alternatively, the pump cavity 210 can define a fluid manifoldthat functions as both the inlet and outlet (e.g., a fluid manifoldfluidly connected to the first and second reservoirs). Inlets andoutlets are preferably defined through the walls of the pump body 240,but can alternatively be defined through the actuating element 220,through the junction between the pump body 240 and the actuating element220, or defined in any other suitable portion of the primary pump 200.An inlet and outlet are preferably located on opposing walls (e.g.,opposing walls extending from the closed end of the pump body 240), butcan alternatively be adjacent on the same wall, be located on the closedend (e.g., of the pump body 240), or be located in any other suitableposition. The inlet and outlet can define an inlet fluid path (e.g.,through which fluid travels into the pump cavity 210) and outlet fluidpath (e.g., through which fluid exits the pump cavity 210),respectively. The inlet and outlet fluid paths are preferably parallel,but can have any suitable relative angle. Additionally or alternatively,the fluid paths can be substantially normal to a radial vector extendingfrom the rotational axis of the drive mechanism 100, but can otherwisebe oriented.

The inlet and outlet of the pump cavity 210 preferably include inlet andoutlet valves (e.g., passively controlled valves, actively controlledvalves operable by the control system 300, etc.) that control fluid flowthrough the respective fluid channels.

However, the pump cavity 210 can be configured in any suitable manner.

3.1.A.ii Actuating Element.

The primary pump 200 can include an actuating element 220 configured toactuate relative the pump cavity 210. The actuating element 220functions to receive the pumping force from the motion transformer 120and to translate within the pump cavity 210, actuating relative to thepump body 240.

The actuating element 220 is preferably operable between a pumping modeand a non-pumping mode. In the pumping mode, the actuating element 220receives a pumping force (e.g., from a drive mechanism 100) andtranslates between a compressed position and a recovered position. Inthe non-pumping mode, the actuating element 220 preferably does notreceive a pumping force (e.g., from the drive mechanism 100) and fluidmovement through the primary pump 200 is ceased and/or hindered. In afirst variation, the actuating element can be operable in a pumping modeduring operation of the stabilization mechanism 550 operation (e.g., inan alleviation mode, in a recovery mode). In a second variation, theprimary pump can be configured to operate in a non-pumping mode inresponse to actuation of a stabilization mechanism 550 (e.g., foralleviating a mass spin state) and/or a pressure regulation mechanism(e.g., for regulating the pressure of the second reservoir), but canalternately operate in the non-pumping mode at any other suitable time.

In a variation where the primary pump is a reciprocating pump, thereciprocating element in the compressed position is preferably proximalthe closed end of the pump cavity 210, and the reciprocating element inthe recovered position is preferably distal the closed end of the pumpbody 240. In this variation, the transition of the reciprocal elementfrom the compression position to the recovered position (e.g., during areturn stroke) can cause a back force applied to the drive mechanism 100that exacerbates the eccentric mass spin.

In a variation where the primary pump is a peristaltic pump, the rotarymotion of a rotor that enables the transition between compressed andrecovered positions can generate a force applied to a coupled drivemechanism 100 that exacerbates the eccentric mass spin.

However, the actuating element 220 can be configured in any suitablemanner.

3.1.A.iii Pump Body.

The pump body 240 of the primary pump 200 functions to cooperativelycompress a fluid with the actuating element 220. The pump body 240preferably defines the pump cavity 210, but can additionally oralternatively define any suitable components. The pump body 240 ispreferably an open pump body 240 with a closed end, where the pump body240 preferably includes a closed end (bottom), walls extending from theclosed end, and an opening opposing the closed end. The walls and endscan be any suitable geometry, and the walls (e.g., openings defined bythe walls) can join the ends at any suitable angle. However, the pumpbody 240 can additionally or alternatively be otherwise configured.

The pump body 240 can be a groove defined in an arcuate or prismaticpiece (e.g., in a longitudinal or lateral direction), a cylinder, aprism, or any other suitable shape. The pump body 240 is preferablysubstantially rigid, but can alternatively be flexible (e.g., when theprimary pump is a peristaltic pump).

The pump body 240 is preferably oriented within the pump system 15 suchthat the closed end is substantially normal to a radial vector extendingfrom the rotational axis of the drive mechanism 100 (e.g., the normalvector from the closed end is substantially parallel to the radialvector), but can alternatively be oriented with the closed end at anangle to the radial vector. The pump body 240 is preferably orientedwith the opening proximal and the closed end distal the drive mechanismrotational axis (e.g., in variations where the primary pump 200 rotatesabout the motion transformer 120 exterior) but can alternatively beoriented with the opening distal and the closed end proximal the drivemechanism rotational axis (e.g., in variations where the primary pump200 rotates about the motion transformer 120 interior), and/or orientedin any other suitable position relative to the drive mechanismrotational axis.

However, the pump body 240 can be configured in any suitable manner.

3.1.B Drive Mechanism

The drive mechanism 100 of the pump system 15 functions to generate thepumping force and to control the magnitude of the pumping force. Thedrive mechanism 100 preferably includes a motion transformer 120 and aneccentric mass 140, but can additionally or alternatively include anysuitable element.

The pumping force (occluding force) is preferably a variable forceapplied in a radial direction from a rotational axis of the drivemechanism 100 (e.g., a cyclic force), but can alternatively be aconstant force, a force applied at any suitable angle to the rotationalaxis, or any other suitable force. The drive mechanism 100 defines arotational axis about which the drive mechanism 100 rotates relative tothe primary pump 200 (conversely, about which the primary pump 200rotates relative to the drive mechanism 100). For example, the drivemechanism 100 (e.g., a motion transformer 120 of the drive mechanism100) can be rotatably coupled to the rotating surface 20 (e.g., mountedto a housing 30 mounted to a surface of the rotating surface 20) aboutthe drive mechanism rotational axis. The rotational axis of the drivemechanism 100 is preferably the rotational axis of the motor transformer120, but can alternatively be the rotational axis of the eccentric mass140, the rotational axis about which the primary pump 200 rotates,and/or any other suitable rotational axis.

The pump system 15 is preferably configured such that the rotationalaxis of the drive mechanism 100 is substantially aligned with therotational axis of the rotating surface 20 when the pump system 15 iscoupled to the rotating surface 20, but the pump system 15 canalternatively be configured such that the rotational axis of the drivemechanism 100 is offset from the rotational axis of the rotating surface20. The drive mechanism 100 preferably defines a drive mechanism centerof mass, determined from the respective mass and positions of the motiontransformer 120 and the eccentric mass 140. The eccentric mass 140 ispreferably coupled to the motion transformer 120 such that the center ofmass of the drive mechanism 100 is offset from the rotational axis ofthe drive mechanism 100.

However, the drive mechanism 100 can be configured in any suitablemanner.

3.1.B.i Motion Transformer

As shown in FIG. 1, the drive mechanism 100 can include a motiontransformer 120 mechanically coupled to the actuating element 220. Themotion transformer 120 functions to convert rotary motion into linearmotion for generating the pumping force for one or more pumps (e.g.,primary pump, secondary pump, etc.). The motion transformer 120 canfunction to provide a substantially constant torque against theeccentric mass 140 throughout the compression stroke (e.g., invariations with a reciprocating pump), but can alternatively provide avariable torque against the eccentric mass throughout the compression orrecovery strokes. The motion transformer can alternatively be omitted(e.g., in non-reciprocating embodiments).

The motion transformer 120 is preferably a cam, but can additionally oralternatively include cranks (e.g., slider cranks), screws (ball screws,roller screws, lead screw, etc.), scotch yokes, pulleys, swashplate,linkages, and/or other suitable motion transformers 120.

The motion transformer 120 preferably includes a bearing surface 122,where the profile of the bearing surface 122 preferably controls themagnitude of the pumping force for a given input torque applied by theeccentric mass 140 and/or the motion transformer 120. The bearingsurface 122 is preferably continuous, but can alternatively bediscontinuous. The bearing surface 122 is preferably defined on theexterior of the motion transformer 120 (exterior bearing surface orouter bearing surface) but can alternatively be defined within theinterior of the motion transformer 120 (interior bearing surface orinner bearing surface), where the bearing surface 122 defines a lumenwithin the motion transformer 120. The bearing surface 122 is preferablyarcuate, and preferably has a non-uniform curvature (e.g., an oblongprofile or a reniform profile. Alternatively, the bearing surface 122can have a uniform curvature (e.g., a circular profile), an angularprofile, or any other suitable profile. As shown in FIGS. 8A-8C, thebearing surface 122 preferably includes a compression portion and arecovery portion, corresponding to the compression stroke and therecovery stroke of the primary pump 200, respectively. The compressionportion is preferably continuous with the recovery section, but canalternatively be discontinuous. The bearing surface 122 preferably has afirst section having a high curvature (preferably positive curvature orconvex but alternatively negative curvature or concave) adjacent asecond section having low curvature (e.g., substantially flat or havingnegative curvature compared to the first section). The bearing surface122 preferably additionally includes a third section connecting thefirst and second sections, where the third section preferably provides asubstantially smooth transition between the first and second sections byhaving a low curvature adjacent the first section and a high curvatureadjacent the second section. However, the bearing surface 122 can haveany suitable profile.

The motion transformer 120 is preferably substantially planar with thebearing surface 122 defined along the side of the motion transformer120, in a plane normal to the rotational axis of the motion transformer120 (e.g., normal the broad face of the motion transformer 120). Thebearing surface 122 is preferably defined along the entirety of themotion transformer side, but can alternatively be defined along aportion of the motion transformer side. The generated pump force ispreferably directed radially outward of the rotational axis, morepreferably along a plane normal to the rotational axis. Alternatively,the motion transformer 120 can have a rounded or otherwise profiled edgesegment (transition between the motion transformer broad face and themotion transformer side), where the bearing surface 122 can include theprofiled edge. Alternatively, the arcuate surface is defined by a faceof the motion transformer 120 parallel to the rotational axis of themotion transformer 120, where the generated pump force can be directedat any suitable angle relative to the rotational axis, varying fromparallel to the rotational axis to normal to the rotational axis.

However, the motion transformer 120 can be configured in any suitablemanner.

3.1.B.ii Eccentric Mass.

The eccentric mass 140 (e.g., hanging mass, hanging pendulum) of thedrive mechanism 100 functions to offset the center of mass of the drivemechanism 100 from the rotational axis of the drive mechanism 100. Thisoffset can function to substantially retain an angular position of thedrive mechanism 100 relative to a gravity vector, thereby engenderingrelative motion between the drive mechanism 100 and the pump systemcomponents that are statically coupled to the rotating surface 20 (whichrotates relative to the gravity vector). The eccentric mass 140 ispreferably a substantially homogenous piece, but can alternatively beheterogeneous. The eccentric mass 140 is preferably a substantiallysingular piece, but can alternatively be made of multiple pieces orsegments. In the latter variation, the multiple pieces are preferablysubstantially similar in shape, angular and radial position, and mass,but can alternatively be substantially different in profile, mass,angular position, or radial position. The eccentric mass 140 ispreferably a distributed mass (e.g., extends along a substantial portionof an arc centered about the drive mechanism rotational axis), but canalternatively be a point mass. The distributed mass can result in higherrotational inertia and/or greater resistance to torque disturbancescaused by a pump (e.g., primary pump 200), which can lead to increasedstability and a longer time period before approaching a mass spin state.In certain applications, particularly those applications when wheelrotational speeds frequently approach the resonant frequency butalternatively any other application, the distributed mass can bepreferable since the distributed mass results in low oscillationfrequencies, thereby resulting in a lower likelihood of eccentric massexcitation into spinning with the system in response to a oscillation(e.g., linear or angular) introduced into the system (e.g., bumps,system pulsation, etc.). The eccentric mass 140 is preferably curved,but can alternatively be substantially flat, angled, or have othersuitable shape. The radius of the eccentric mass curvature is preferablymaximized (e.g., relative to or up to the pump system radius), such thatthe eccentric mass traces an arcuate section of the pump systemperimeter. However, the eccentric mass 140 can have any other suitablecurvature.

The eccentric mass 140 is preferably a separate piece from the motiontransformer 120, and is preferably coupled to the motion transformer 120by a mass couple 142. Alternatively, the eccentric mass 140 can beincorporated into the motion transformer 120, where the eccentric mass140 is incorporated along the perimeter of the motion transformer 120,incorporated into a half of the motion transformer 120, or incorporatedalong any other suitable portion of the motion transformer 120. Theeccentric mass 140 can be statically coupled to the motion transformer120 or rotatably coupled to the motion transformer 120 (e.g., by a setof bearings, a rotary union, etc.). In the variation where the eccentricmass 140 is statically coupled to the motion transformer 120, theeccentric mass 140 can be coupled to the motion transformer 120 at therotational axis of the motion transformer 120, at the rotational axis ofthe drive mechanism 100, offset from the rotational axis of the motiontransformer 120, or at any other suitable portion of the motiontransformer 120. The eccentric mass 140 can be permanently connected tothe motion transformer 120. Alternatively, the eccentric mass 140 can betransiently connected (removably coupled) to the motion transformer 120(e.g., by a clutch mechanism, ratcheting mechanism, etc.), where theeccentric mass 140 can be operable between a pumping mode where theeccentric mass 140 is coupled to the motion transformer 120 and anon-pumping mode where the eccentric mass 140 is disconnected from themotion transformer 120. The eccentric mass 140 preferably has a highmoment of inertia, but can alternatively have a low moment of inertia.

The mass couple 142 is preferably a disk, but can alternatively be alever arm, plate, or any other suitable connection. The mass couple 142preferably couples to the broad face of the motion transformer 120, butcan alternatively couple to the edge of the motion transformer 120,along the exterior bearing surface of the motion transformer 120, to theinterior bearing surface of the motion transformer 120, to an axleextending from of the motion transformer 120 (where the motiontransformer 120 can be statically fixed to or rotatably mounted to theaxle), or to any other suitable portion of the motion transformer 120.The mass couple 142 can couple to the motion transformer 120 byfriction, by a transient coupling mechanism (e.g., complimentaryelectric or permanent magnets located on the motion transformer 120 andmass couple 142, a piston, a pin and groove mechanism, etc.), bybearings, or by any other suitable coupling means. When the mass couple142 couples to the motion transformer 120 by a transient couplingmechanism, the mass couple 142 is preferably operable between a coupledmode, where the mass couple 142 connects the eccentric mass 140 to themotion transformer 120, and a decoupled mode, where the mass couple 142disconnects the eccentric mass 140 from the motion transformer 120. Themass couple 142 can additionally function as a shutoff mechanism, wherethe mass couple 142 is switched from the coupled mode to the decoupledmode in response to the detection of a shutoff event (e.g., thereservoir pressure reaching a threshold pressure). In one variation, themass couple 142 is a disk located within the lumen defined by aninterior bearing surface of the motion transformer 120, where the diskcan rotate relative to the interior bearing surface in the decoupledmode and is coupled to the interior bearing surface by a frictionelement in the coupled mode. In another variation, the mass couple 142is rotatably mounted on an axle extending from the motion transformer120 by bearings, where the mass couple 142 can be statically coupled tothe motion transformer 120 by one or more sets of magnets or pistonsextending from the adjacent broad faces of the motion transformer 120and mass couple 142.

However, the eccentric mass 140 and the mass couple 142 can beconfigured in any suitable manner.

3.1.C Motion Transformer Couple

The pump system 150 can include a motion transformer couple 130, whichfunctions to connect the primary pump 200 (e.g., the actuating element220 of the primary pump) to the drive mechanism 100 (e.g., the motiontransformer 120 of the drive mechanism 100). The motion transformercouple 130 (e.g., force translator) can additionally or alternativelyfunction to translate relative motion between the drive mechanism 100and the primary pump 200 into a variable occluding force.

The motion transformer couple 130 is preferably a cam follower (e.g., acam roller, cam bearing, etc.), but can additionally or alternatively bea keyed piece (e.g., tooth and gear complimentary pieces joining thedrive mechanism 100 and the primary pump), linkage (e.g., rotatablelinkage), and/or any suitable coupling mechanism.

The motion transformer couple 130 preferably applies a force in aradially outward direction from the rotational axis, but canalternatively apply a force in a radially inward direction, in adirection substantially parallel to the rotational axis, in a directionat an angle to the rotational axis, or in any other suitable direction.The motion transformer couple 130 preferably includes an axis having anarcuate position that is fixed relative to an arcuate position of theprimary pump 200 (the angular position of the motion transformer couple130 axis about the rotational axis is preferably fixed relative to theangular position of the primary pump 200). More preferably, the motiontransformer couple 130 or a portion thereof has an angular positionfixed to and substantially similar to the angular position of theprimary pump 200 about the rotational axis, such that the motiontransformer couple 130 travels with the primary pump 200 about therotational axis.

The motion transformer couple 130 is preferably configured to travelalong the arcuate bearing surface 122 of the motion transformer 120(e.g., cam). The motion transformer couple 130 preferably maintains asubstantially constant distance between the arcuate bearing surface 122and the actuating element 220, such that the motion transformer couple130 applies a variable force against the actuating element 220 as themotion transformer couple 130 travels along the variable curvature ofthe arcuate bearing surface 122 of the motion transformer 120. Themotion transformer couple 130 is preferably in non-slip contact with thearcuate bearing surface 122, but can alternatively slide along thearcuate bearing surface 122. As such, the motion transformer 120 ispreferably rotatably coupled to the bearing surface of the motiontransfer. Further, the motion transformer couple 130 is preferablyrotatably coupled to the actuating element 220, but can alternatively beotherwise coupled.

In a variation where the primary pump 200 is a reciprocating pump, thereciprocating element is a piston, and the motion transformer couple 130is a roller, the reciprocating element 220 preferably rotatably connectsto the roller at the rotational axis of the roller, but can connect tothe roller with a semi-circular cup that cups the roller, or through anyother suitable coupling mechanism. In a variation where the primary pump200 is a reciprocating pump and the reciprocating element is adiaphragm, the reciprocating element 220 can directly contact thediaphragm, couple to the diaphragm through a piston, or couple to thediaphragm in any other suitable manner.

In a variation, the primary pump 200 can be a peristaltic pump and themotion transformer couple 130 can be a planetary roller that rolls aboutan interior or exterior arcuate surface of the motion transformer 120(e.g., as disclosed in U.S. application Ser. No. 13/187,848, filed 21Jul. 2011, incorporated herein in its entirety by this reference.

However, the motion transformer couple 130 can be configured in anysuitable manner.

3.2 Stabilization Mechanism

The tire inflation system 10 includes a stabilization mechanism 550 thatfunctions to compensate for forces applied by the primary pump 200 onthe driving mechanism (e.g., a motion transformer 120 of the drivingmechanism). The stabilization mechanism 550 can additionally oralternatively function to reduce and/or prevent eccentric mass spin(e.g., during a mass spin state). In the mass spin state, the eccentricmass preferably rotates (e.g., spins) with the rotating surface 20.Additionally or alternatively, in the mass spin state, the eccentricmass can be in any state hindering the generation of a pumping forcefrom the relative motion between the eccentric mass and a rotatingsurface, but the mass spin state can be otherwise defined.

As shown in FIGS. 2A-2C, the stabilization mechanism 550 is preferablyactively operable (e.g., controlled by a processing system 320) betweenan alleviation mode (e.g., where the stabilization mechanism 550alleviates back force applied from the primary pump 200 on the drivingmechanism) and a recovery mode (e.g., where the stabilization mechanism550 enables the tire inflation system 10 to transition back into anon-mass spin state). The stabilization mechanism 550 is preferablyconfigured to enter an alleviation mode (e.g., from a processing system320 actively actuating the stabilization mechanism 550) in response toparameters (e.g., eccentric mass spin parameters measured by a sensorset 310) indicating a mass spin state. Additionally or alternatively,the stabilization mechanism 550 can be configured to enter thealleviation mode in response to an unstable state of the motiontransformer, the motion transformer couple, the mass couple 142, and/orany other suitable component. However, the stabilization mechanism 550can be configured to enter the alleviation mode in response to anysuitable trigger event. Additionally or alternatively, the stabilizationmechanism 550 can be passively operated and/or otherwise operated.

The stabilization mechanism 550 is preferably a fluid valve configuredto selectively vent the pump cavity 210, but can additionally oralternatively include a clutch mechanism, the eccentric mass 140, themass couple 142, the motion transformer 120, the motion transformercouple 130, and and/or other suitable components. The pump system 15 caninclude any combination of stabilization mechanisms 550. The pump system15 can include a plurality of stabilization mechanisms 550 configured tooperate in parallel, serial, and/or at any suitable time. For example,the pump system 15 can include a primary stabilization mechanism 550(e.g., a fluid valve), and a secondary stabilization mechanism 550(e.g., a clutch mechanism) configured to be actively actuated by theprocessing system 320 in response to failure of the primarystabilization mechanism 550 to sufficiently reduce eccentric mass spin.

However, the stabilization mechanism 550 can be configured in anysuitable manner.

3.2.A Stabilization Mechanism—Fluid Valve

In an embodiment, the stabilization mechanism 550 can include one ormore fluid valves (e.g., stabilization valves), which function toselectively vent (e.g., purge) the pump cavity 210 and/or other suitablecomponents to reduce back pressure applied to the driving mechanism. Forexample, in some circumstances, the back force that can cause theeccentric mass 140 to enter a mass spin state can be reduced by releaseof pressure within the primary pump 200 (e.g., release of pressurewithin a pump cavity 210, within a pump lumen, etc.), which can in somevariations be accomplished by opening a suitable fluid valve (or fluidvalves).

As shown in FIGS. 1 and 6, the fluid valve is preferably fluidlyconnected with the pump cavity 210 of the primary pump 200 (e.g.,configured to release fluid from the pump cavity 210), but canadditionally or alternatively be fluidly connected to any suitablecomponent for alleviating unstable eccentric mass movement. Further, thefluid valve is preferably fluidly connected with one or more fluidreservoirs (e.g., configured to release fluid into the fluid reservoir).For example, the fluid valve can define a fluid path fluidly connectingthe pump cavity 210 to the fluid reservoir (e.g., a fluid path beginningat the pump cavity 210 and ending at the fluid reservoir). The fluidreservoir can include: the ambient environment, the interior of thehousing 30 (where the housing 30 functions as a pressurized first fluidreservoir 400 that can be recirculated back into the second reservoir500), the tire interior, and/or any other suitable fluid reservoir.

The fluid valve is preferably operable between an open position and aclosed position (e.g., any position between and including fully open andfully closed). The fluid valve preferably allows fluid to travel throughthe fluid valve in the open position, and preferably restricts fluidtravel through the fluid valve in the closed position. In particular,the fluid valve preferably includes a valve actuator configured totransition the fluid valve between the open and closed positions. Thefluid valve can be configured to enter the open position in response todetection of a mass spin state and/or imminent mass spin, and to enterthe closed position in response to sufficient alleviation of the massspin state (e.g., detection of a non-spin state or mass spin state exit)and/or the imminent mass spin. During the mass spin state and/orimminent mass spin, the fluid valve can be configured to operate in theopen position during the entire period or a partial period of the massspin state (e.g., while the measured parameters continue to indicate aneccentric mass spin state) and/or imminent mass spin. In a variation,the fluid valve can be configured to operate in the open positionconcurrently with the primary pump 200 operating in recovery mode (e.g.,during a actuating element's recovery stroke, which can apply the backforce on the drive mechanism 100), and to operate in the closed positionconcurrently with the primary pump 200 operating in compression mode.However, the fluid valve can operate in any suitable mode at anysuitable time.

The fluid valve is preferably an active valve, but can alternatively bea passive valve (e.g., passively controlled). Examples of fluid valvesthat can be used include: electric control valves, centrifugal forcevalves, spring-based valves, pneumatic valves, hydraulic valves, and/orany other suitable type of valves.

When the fluid valve is an active valve, the fluid valve (e.g., a valveactuator of the fluid valve) is communicably coupled (e.g., throughelectrical wiring, through a wireless communications module 350 of thefluid valve, etc.) to the processing system 320 of the control system300, which can be configured to actively actuate (e.g., turn, providetorque to, etc.) the fluid valve to transition the fluid valve betweenopen and closed modes (e.g., alleviation and recovery modes). However,the fluid valve can be otherwise controlled.

In a variation, the fluid valve is an electric control valve. Theelectric control valve preferably includes an electric actuatorelectrically connected to the processing system 320 and configured toprovide an actuation force to a valve actuator in operating between openand closed positions. The actuation force can be a rotational force, alinear force, or be any other suitable force. For example, theprocessing system 320 can be configured to apply an electric current toa solenoid of the electric control valve in response to detection of amass spin state and/or imminent mass spin, where the electric controlvalve is configured to operate the electric motor to actuate the fluidvalve (e.g., open the fluid valve to relieve pump cavity 210 fluidpressure) in response to the applied electric current. Examples ofelectronic control valves that can be used include: solenoid controlvalves, dual solenoid control valves, single point insertion flowmetering valves, electric actuator valves, or any other suitable type ofelectronic control valve. The electronic control valves can be actuatedmagnetically (e.g., energizing a solenoid which induces a magnetic fieldwithin along the central axis of the solenoid), electronically (e.g.,through a direct wire electronic connection), via wirelesselectromagnetic communication (e.g., through a radio transmission), orin any other suitable actuation-initiating manner.

In another variation, the fluid valve is a pneumatic valve configured toconvert pneumatic energy into mechanical motion for operating thepneumatic valve. The pneumatic valve is preferably an actively operatedpneumatic valve. For example, the pneumatic valve can include a valvefluid reservoir, a valve actuator (e.g., piston or diaphragm) fluidlyconnected to the valve fluid reservoir and configured to operate thevalve in response to receiving fluid pressure from fluid in the valvefluid reservoir, where the processing system 320 is configured tocontrol the valve fluid reservoir to release fluid for actuating thevalve actuator. In another example, the pneumatic valve can beelectrically connected to a pressure transmitter configured to monitorpressure in the pump cavity 210, and to transmit a fluid at apredetermined fluid pressure in response to the pressure transmittermeasurements exceeding a pressure threshold (e.g., corresponding toeccentric mass spin). Alternatively, the pneumatic valve can be apassively operated pneumatic valve. For example, the pneumatic actuatorcan be a spring-opened pneumatic actuator configured to operate in anopen mode in response to fluid pressure overcoming the spring pressurethreshold (e.g., corresponding to eccentric mas spin) to actuate thepneumatic valve. However, the pneumatic valve can be otherwiseconfigured.

In another variation, the fluid valve is a spring-based valve operablebetween open and closed positions based upon spring position (e.g.,relaxed, compressed, stretched, etc.). The spring-based valve ispreferably an actively operated spring-based valve. For example, thespring-based valve can include an electrically controlled springoperable between relaxed and stretched positions based on the magnitudeof an excitation current (e.g., controlled by an electrically connectedprocessing system 320) applied to the spring. In this example, thespring-based valve can be configured to release fluid from the fluidcavity at different rates based on spring position. In another example,the processing system 320 can be configured to control the spring-basedvalve to release the spring, thereby operating the valve, in response topower loss (e.g., which can be correlated with an unstable mass spinstate effecting power provision by the power module). However, thespring-based valve can be passively controlled and/or otherwiseoperated.

In another variation, the fluid valve is a passive centrifugal forcevalve operable between open and closed positions based on the amount ofapplied centrifugal force. For example, the centrifugal force valve canbe configured to open along an actuation axis in response to applicationof a centrifugal force exceeding a cracking force, the cracking forceselected based on the centrifugal force generated by wheel rotation ator near a resonant frequency of the drive mechanism 100. The centrifugalforce valve can include a valve mass element that acts as a valveactuator. The valve mass element can define an actuation axis alignedwith a centrifugal force vector generated from wheel rotation speed nearthe drive mechanism 100 resonant frequency, where the valve mass elementis configured to actuate along its actuation axis (e.g., as guided by acompliant element such as a spring physically connected to the valvemass element) in response to the centrifugal force vector exceeding acracking force, thereby actuating the valve into an open position.Further, the valve mass element can be configured to return along itsactuation axis to its original position, in response to the centrifugalforce vector below the cracking position, thereby returning the valveinto a closed position. In this variation, the centrifugal force valvecan be mounted to the housing 30 and arranged with the actuation axissubstantially radially aligned relative to the drive mechanismrotational axis. However, the passive centrifugal force valve can beconfigured in any manner.

The fluid valve is preferably positioned proximal the pump cavity 210and the fluid reservoir. In a variation, the fluid valve is positionedat or fluidly connected to the pump body 240 (e.g., mounted to thehousing, embedded with the pump body 240). The fluid valve can include afirst end defined by a wall or closed end of the pump body 240, a secondend fluidly connected to the fluid reservoir, and a fluid valve actuatorconfigured to open and/or close the fluid path connecting the first andsecond ends. In another variation, the fluid valve can be positionedproximal a lumen cooperatively defined by the pump cavity 210 and theactuating element 220 (e.g. where the actuating element 220 isconfigured to perform compression strokes and/or recovery strokesthrough the lumen). The fluid valve can include an end defined by alumen wall (e.g., a portion of the lumen wall proximal the closed end ofthe pump body 240, a portion of the lumen wall proximal the motiontransformer couple 130, etc.). In a variation where the pump is areciprocating pump, the fluid valve can be positioned at or fluidlyconnected to the pump chamber of the reciprocating pump (e.g., a closedend of the pump chamber). In a variation where the pump is a peristalticpump, the fluid valve can be positioned at or fluidly connected to thetube or diaphragm actuating element 220. For example, the fluid valvecan include an end physically connected to a portion of the tube wall.In this variation, the fluid valve can additionally or alternatively bepositioned at or fluidly connected to the groove (e.g., where the rotoris located) and proximal the rotor. However, the fluid valve andcomponents of the fluid valve can be located at any suitable locationrelative the pump system 15. In a variation where the pump system 15includes a plurality of pumps (e.g., a secondary pump, a tertiary pump,etc.), the fluid valve can be positioned at any suitable locationrelative the non-primary pumps (e.g., positioned at a pump cavity 210 ofthe secondary pump). In one embodiment, one fluid valve can be connectedto one or more of the multiple pump cavities. In a second embodiment,each pump cavity can be connected to a different fluid valve. As shownin FIG. 5, in a variation where the pump system 15 includes a primarypump 200 a, a secondary pump 200 b, the fluid valve can be fluidlyconnected to a fluid manifold fluidly connecting the pump cavities ofthe respective pumps 200 a, 200 b. Alternatively, as shown in FIG. 7,the fluid valve can be fluidly connected with the pump cavity of thesecondary pump 200 b. However, the fluid valve can be otherwisepositioned relative a secondary pump 200 b and/or a fluid manifold 202.

The tire inflation system 10 preferably includes electrical wiringpositioned between and electrically connecting the fluid valve and theprocessing system 320. In a variation, the electrical wiring can besubstantially parallel the drive mechanism rotational axis (e.g., wherethe processing system 320 is aligned with the fluid valve along analignment axis parallel the rotation axis and/or along an axis normal toa face of the housing interior. In another variation, the electricalwiring can be parallel a radial vector extending from the drivemechanism rotational axis. Additionally or alternatively, the electricalwiring can be angled in any suitable configuration relative componentsof the tire inflation system 10.

The fluid valve can define a fluid path substantially parallel a radialvector extending from the rotation axis of the driving mechanism (e.g.,in a fluid valve positioned at a closed end of the pump body 240) and/oran actuation axis of the actuating element 220 (e.g., in a reciprocatingpump). Alternatively, the fluid path can be substantially normal theradial vector (e.g., in a fluid valve positioned at a wall of the pumpbody 240), but can be at any suitable angle to any suitable axes and/orreference feature.

The fluid valves of the stabilization mechanism 550 can be functionaldirectional control valves, The fluid valves are preferably one-wayvalves (e.g., configured to release fluid from the fluid cavity into areservoir) but can alternatively be two-way valves, three-way valves,two-way/two-position (“2-2”) valves, and/or possess any suitabledirectionality characteristic. The fluid valves can have two-ports(e.g., a check valve), three-ports (e.g., shuttle valves), or anysuitable number of ports (e.g., a valve which compares pressures at someports and permits or inhibits fluid flow based on a comparison of inputpressures). The fluid valves can have a substantially circular crosssection, a substantially square cross section, or any other suitableshape. The fluid valves can be made of brass alloys, stainless steel,carbon steel, nickel alloys, titanium alloys, copper alloys,corrosion-resistant materials, substantially fluid impermeablematerials, cost-effective materials, or any other suitable type ofmaterial. However, the valves can have any suitable geometry and shapeto facilitate pressure relief from the pump cavity 210.

Additionally or alternatively, the fluid valves can be configured in anysuitable manner.

3.2.B Stabilization Mechanism—Clutch Mechanism

In another embodiment, the stabilization mechanism 550 can include oneor more clutch mechanisms, which function to mechanically engage and/ordisengage components of the pump system 15 to hinder the pump system'stranslation of rotational motion into linear motion, in order toalleviate forces applied by the primary pump 200 on the drive mechanism100.

The clutch mechanism is preferably operable between an engaged mode anda disengaged mode. The clutch mechanism preferably includes a drivingmember mechanically coupled (e.g., transiently coupled) with a drivenmember in the engaged mode, and preferably includes a driving membermechanically decoupled (e.g., transiently decoupled) from the drivenmember in the disengaged mode. Further, the clutch mechanism ispreferably configured to mechanically actuate the driving member and/orthe driven member to mechanically engage (e.g., facilitate motiontransfer) or disengage pump system components mechanically coupled tothe clutch mechanism. Additionally or alternatively, the clutchmechanism can engage and/or disengage (e.g., mechanically,hydraulically, etc.) any suitable components.

In a first variation, the clutch mechanism is configured to mechanicallyengage and/or disengage components of the primary pump 200 fromcomponents of the drive mechanism 100. In an example, the inflationsystem can include a clutch mechanism positioned between andmechanically coupled to the motion transformer couple 130 and the motiontransformer 120. In a specific example, the driving member ismechanically coupled to the motion transformer couple 130, and thedriven member is mechanically coupled to the motion transformer 120. Inanother specific example, the clutch mechanism can include an actuatingelement 220 coupled normally to a face of the motion transformer 120(e.g., cam module) and configured to actuate the motion transformer 120out of alignment with the motion transformer couple 130, where in theclutch mechanism disengaged mode, the motion transformer 120 ismisaligned from the motion transformer couple 130 along a radial vectorextending from the rotation axis. In another example, the clutchmechanism can include an actuation element mechanically coupled to themass transformer couple and/or the mass transformer, and configured toactuate the mass transformer couple and/or the mass transformer alongthe radial vector extending from the rotational axis of the drivemechanism, where in the disengaged mode, the mass transformer couple andmass transformer are mechanically decoupled and radially aligned alongthe radial vector. In another example, the clutch mechanism can bearranged between the drive mechanism (e.g., between the mass transformerand the system housing), wherein clutch engagement connects the drivemechanism to one or more gears that control drive mechanism rotation. Ina specific example, the clutch can be engaged when a mass spin state(e.g., current or imminent) is detected, wherein clutch engagement slowsand/or controls mass transformer and eccentric mass rotation about thepump system. In other examples, the clutch mechanism is mechanicallycoupled to the primary pump 200 and configured to actuate the primarypump 200 relative the mass transformer.

In another variation, the clutch mechanism is configured to mechanicallyengage and/or disengage components of the pump system 15 from therotating surface 20. For example, the clutch mechanism can be positionedbetween the rotating surface 20 and the primary pump 200, the clutchmechanism including a driving member statically coupled to the rotatingsurface 20, and a driven member mechanically coupled to the primary pump200. In a specific example, the primary pump 200 can include a frictionsurface transiently coupled to the rotation surface, and a clutchmechanism mechanically coupled to the primary pump 200 and configured toactuate the primary pump 200 along an axis normal to a face of thefriction surface, where in the clutch mechanism disengaged mode, theprimary pump friction surface is mechanically decoupled from therotating surface 20.

The clutch mechanism is preferably an actively controlledelectromagnetic clutch mechanism. Additionally or alternatively, theclutch mechanism can be a passively controlled clutch (e.g., acentrifugal clutch mechanism), and/or other suitable clutch mechanism(e.g., hydraulic clutch, belt clutch, dog clutch, wrap-spring clutchetc.). The clutch mechanism is preferably electrically connected to theprocessing system 320, which can be configured to control operation ofthe clutch mechanism (e.g., transition the clutch mechanism betweenengaged and disengaged mode). In an example, the inflation system caninclude an electromagnetic clutch mechanism including a magnetizablerotor magnetically coupled to an armature, the armature mechanicallycoupled to a driven member (e.g., a mass transformer couple, a masstransformer, etc.), and a processing system 320 configured to apply acurrent to the electromagnetic clutch to generate a magnetic field(e.g., in response to a stabilization mechanism 550 alleviation modetriggering event), where the armature is frictionally coupled to therotor in the engaged mode, and frictionally decoupled from the rotor thedisengaged mode.

However, the clutch mechanism can be configured in any suitable manner.

3.2.C Stabilization Mechanism 550—Couple

In another embodiment, the stabilization mechanism 550 can be the masscouple 142, the motion transformer couple 130, and/or any other suitablecouples between components of the pump system 15 and/or the rotatingsurface 20. In this embodiment, the stabilization mechanism 550 coupleis preferably an electrically controlled actuatable coupling mechanism,which can be electrically connected to the processing system 320 (e.g.,configured to actively control the coupled state and decoupled statebetween components), and configured to actuate one or more mountedcomponents. In a variation, the electronically controlled actuatablecoupling mechanism can be configured to couple and/or decouple themounted components (e.g., decouple the motion transformer couple 130from the motion transformer 120 to prevent back force applied by themotion transformer couple 130 to the motion transformer 120). In anothervariation, the electronically actuatable coupling mechanism can actuatethe eccentric mass 140 and/or the motion transformer 120 along the,which can reduce static unbalance and prevent the eccentric mass 140from reaching a mass spin state. For example, the eccentric mass 140 canbe mechanically coupled to the motion transformer 120 through anelectrically controlled adjustable rod configured to actuate theeccentric mass 140 closer to the motion transformer 120 (e.g., through aprocessing system 320 configured to control the adjustable rod inresponse to detecting a mass spin state and/or imminent mass spin).

However, any suitable couple can be otherwise configured as astabilization mechanism 550.

3.2.D Stabilization Mechanism—Vehicle

In another embodiment, the stabilization mechanism 550 can include thevehicle to which the rotating surface 20 is attached. In thisembodiment, the control system 300 is preferably communicably coupled tothe vehicle (e.g., through an on-board diagnostics port, wirelessly witha vehicular communication system, etc.). In a variation, the vehicle isa master device, and the control system 300 is the slave device. In thisvariation, the vehicle can be configured to detect a mass spin stateand/or imminent mass spin (e.g., based on vehicle sensors such as avehicle camera oriented towards the eccentric mass 140, based onvehicular speed indicating a mass spin state and/or imminent mass spin,etc.). The vehicle can be configured to communicate with the controlsystem 300 (e.g., controlling the control system 300 to actuate a fluidvalve stabilization mechanism 550) in response to the vehicle detectingthe mass spin state and/or imminent mass spin. Alternatively, thevehicle can control itself (e.g., decelerate), and/or perform anysuitable action for alleviating a mass spin state and/or imminent massspin. In another variation, the control system 300 is the master device,and the vehicle system is the slave device. In this variation, thecontrol system 300 can include a processing system 320 configured tocommunicate with the vehicular control system 300 (e.g., notifying thedriver at an interface of the vehicle to slow down, controlling thevehicle to decelerate) in response to a triggering event (e.g.,detecting an eccentric mass 140 state based on collected sensor data).In another variation, the tire inflation system 10 can be communicablycoupled (e.g., though a Bluetooth wireless connection) with a userdevice (e.g., a user smartphone), and configured to automatically promptthe user to perform an action (e.g., decelerate, pull over, etc.) tostabilize a mass spin state and/or imminent mass spin.

However, the vehicle can be otherwise configured as the stabilizationmechanism 550.

3.3 Control System.

As shown in FIGS. 2A-2C, the tire inflation system 10 includes a controlsystem 300, which can include a sensor set 310, a processing system 320,power module, and/or a communications module 350. The control system 300functions to control operation of the stabilization mechanism 550 (e.g.,in response to detecting a mass spin state and/or imminent mass spin).The control system 300 preferably actively controls operation of thestabilization mechanism 550 (e.g., controlling the stabilizationmechanism with the processing system 320), but can additionally oralternatively passively control operation of the stabilization mechanism550 (e.g., where the control system includes a passively-activated valveactuator, such as the inertia imparted on the disc of a valve, etc.).The control system 300 can additionally or alternatively function tocollect sensor measurements, process sensor measurements, and/ordetermine a mass spin state and/or imminent mass spin. However, thecontrol system 300 can be configured in any suitable manner.

3.3.A Control System—Sensor Set

As shown in FIGS. 1, 2A-2C, and 3A-3B, the control system 300 caninclude a sensor set 310 configured to measure an eccentric massparameter. The sensor set 310 functions to monitor one or moreparameters indicative of eccentric mass spin. The sensor set 310 caninclude any number of sensors.

The sensor set 310 preferably monitors one or more eccentric massparameters indicative of a mass spin state and/or imminent mass spin.Eccentric mass parameters can include any one or more of: inflationsystem parameters (e.g., pump system parameters, drive mechanismparameters, etc.), rotational surface parameters (e.g., wheelparameters, hub parameters, etc.), vehicle parameters, ambientparameters, or any other suitable parameter. Examples of monitoredparameters include: temperature, humidity, pressure, viscosity,velocity, angular movement (e.g., acceleration, velocity, displacement,etc.; of the eccentric mass 140, motion transformer 120, drive mechanism100, housing 30, tire, etc.), radial movement (e.g., acceleration,velocity, displacement, etc.; of the eccentric mass 140, motiontransformer 120, drive mechanism 100, housing 30, tire, etc.), force,centripetal force, centrifugal force, acceleration (e.g., lateralacceleration, relative to a gravity vector, etc.), torque, displacement,or any other suitable system parameter indicative of a mass spin stateand/or imminent mass spin.

The sensor set 310 is preferably communicably connected (e.g., throughelectrical wiring, through a wireless communication module of the sensorset 310, etc.) to the processing system 320. The processing system 320is preferably configured to control operation of the sensor set 310(e.g., control the sensor set 310 to collect sensor data, control thesensor set 310 to re-position and/or re-orient itself, etc.). Further,the processing system 320 is preferably configured to receive sensordata collected at one or more sensors of the set. In a variation wherethe sensor set 310 includes a plurality of sensors, the processingsystem 320 can control the plurality of sensors individually (e.g.,control an angular velocity sensor to monitor angular velocity of theeccentric mass 140 in response to vehicular speed above a threshold, andto control a pressure sensor to continuously monitor primary pump fluidpressure), in aggregate, and/or in any suitable manner. Additionallyand/or alternatively, the pump system 15 can include one or more sensorscommunicatively coupled to the stabilization mechanism 550.

The sensor set 310 is preferably mounted to the monitored component(e.g., a pressure sensor mounted to the primary pump cavity 210 andconfigured to monitor the fluid pressure in the primary pump cavity210), but can alternatively be mounted to an opposing surface or to anyother suitable mounting point. For example, as shown in FIGS. 3A-3B, thesensors can be mounted to the housing 30 (e.g., interior or exterior),to the drive mechanism 100, to the eccentric mass 140, to the motiontransformer 120, to the primary pump 200, or to any other suitablecomponent of the pump system 15. When the sensor is mounted to acomponent that moves relative to the processing system, the sensor dataconnection can extend along the component, through the axis of rotation,and along the housing to the processing system. Alternatively, data canbe transferred through a rotary union or any otherwise transferred.

In a first variation, the sensor set 310 can include a motion sensor(e.g., gyroscope, accelerometer, rotary sensor, optical sensors,orientation sensors, displacement sensors, magnetometers, etc.). Themotion sensor is preferably mounted on the eccentric mass 140, but canadditionally or alternatively be mounted on the mass couple 142, themotion transformer 120, and/or other suitable component. In a firstexample of the first variation, the motion sensor can be configured tomeasure the angular velocity of the eccentric mass 140 about arotational axis of the drive mechanism Dm. In this example, the sensorset 310 can include a gyroscope mounted to the eccentric mass 140 anddefining an axis (e.g., a z-axis) substantially parallel the rotationalaxis of the drive mechanism 100. In this example, the gyroscope can bemounted to a face of the eccentric mass 140 proximal a face of thehousing interior, and electrically connected (e.g., through electricalwiring) to a processing system 320 mounted to the face of the housinginterior.

In another example of the first variation, the sensor set can include anoptical rotary encoder. In this example, the tire inflation system 10can include a processing system 320 configured to translate a lightpattern into an angular parameter (e.g., angular position, angularvelocity, etc.) of the eccentric mass 140, and a sensor set 310including an optical rotary encoder including a optical sensor (e.g.,photodetector, camera, etc.) configured to receive the light pattern,and/or a light source (e.g., an LED light source). In a first specificexample, the tire inflation system 10 can include a optical sensorpositioned on the eccentric mass 140, a light source positioned on thehousing 30 (e.g., interior face of the housing 30), and a processingsystem 320 configured to determine an angular parameter (e.g., angularvelocity) based on the rate at which light (emitted by the light source)is detected at the optical sensor. In a second specific example, theoptical sensor can be positioned on the housing 30, and the light sourcecan be positioned on the eccentric mass 140. In a third specificexample, the optical sensor and the light source can be positioned onthe housing 30, where the light source can be oriented to emit lighttowards a drive mechanism 100 (e.g., towards the eccentric mass),wherein the drive mechanism 100 includes a visually distinguishableelement (e.g., a reflective region producing a light pattern), andwherein the processing system 320 is configured to determine an angularparameter (e.g., angular velocity) based on data collected by theoptical sensor (e.g., data analyzed to determine the periodicity oflight reflectance, the periodicity of light dimming, etc.). In a fourthspecific example, the optical sensor and the light source can bepositioned on the eccentric mass 140, where the light source can beoriented to emit light towards the housing 30 (e.g., an interior face ofthe housing), wherein the housing includes a visually distinguishableelement. Alternatively, the rotating encoder element can be theeccentric mass 140 (e.g., where the light source is positioned betweenthe motion transformer 120 and a face of the eccentric mass 140, and thephoto detector is positioned between the opposing face of the eccentricmass 140 and a face of the housing interior. However, the optical rotaryencoder can be otherwise configured.

In another example of the first variation, the tire inflation system 10can include an optical sensor (e.g., camera module) mounted to thehousing 30. For example, the optical sensor can be mounted to aninterior of the housing 30 and oriented with a field of view directedtowards the eccentric mass 140, where the processing system 320 isconfigured to process images captured by the optical sensor to determinea relative motion parameter describing relative motion between theeccentric mass 140 and the housing 30, and to determine a mass spinstate and/or imminent mass spin based on the relative motion parameter.Alternatively the optical sensor can be mounted to the eccentric mass140. For example, the optical sensor can be mounted to a face of theeccentric mass 140 proximal the interior housing, the optical sensororiented with field of view directed towards the interior housing.

In another example of the first variation, the sensor set 310 caninclude a speedometer. The speedometer can be configured to measure thetranslational velocity of the housing 30, which can be indicative of thevehicle speed. The speedometer can be mounted to the housing 30, mountedto the rotating surface 20, mounted to the vehicle (e.g., where thespeedometer can be the vehicle speedometer, where the processing system320 connects to the vehicle speedometer through an in-hub or in-axleconnection), or be otherwise arranged. In this variation, thetranslational velocity of the housing 1710 can be used to infer theangular velocity of the eccentric mass 140 (e.g., the angular velocityof the eccentric mass 140 can have a characteristic dependence on thetranslational velocity of the housing 1710 that can permit inferring theformer from the latter). In this example, the tire inflation system 10can include a processing system 320 configured to determine that theeccentric mass 140 is in and/or approaching the mass spin state inresponse to the translational velocity of the housing 30 falling withina mass spin velocity range, wherein the mass spin velocity range isdefined by a lower velocity threshold and an upper velocity thresholdencompassing a characteristic velocity characterizing a resonantfrequency of the drive mechanism. In a specific example, the processingsystem 320 can be configured to determine imminent mass spin in responseto the translational velocity falling within a first mass spin velocityrange, and/or to determine a mass spin state in response to thetranslational velocity falling within a second mass spin velocity range.The second mass spin velocity range preferably include an upperthreshold greater than the upper threshold of the first mass spinvelocity range, but can alternatively be smaller. The first and secondmass spin velocity ranges can be overlapping, non-overlapping, and/orotherwise defined. However, the motion sensor can be configured in anysuitable manner.

In a second variation, the sensor set 310 can include a pressure sensorconfigured to measure a fluid pressure indicative of current and/orimminent mass spin. The pressures sensor is preferably mounted to aprimary pump component (e.g., pump cavity 210, pump lumen, etc.), thatthe pressures sensor is configured to monitor, but can additionally oralternatively be mounted to a fluid reservoir, and/or any suitablecomponent. The pressure sensor measurement can be used to determine(e.g., infer) current and/or imminent mass spin. For example, currentand/or imminent mass spin can be determined in response to the pressuresensor measurement value exceeding a threshold pressure value. Thethreshold pressure value can be: pre-set (e.g., by a manufacturer),user-determined, automatically learned, or otherwise determined. A firstthreshold pressure value corresponding to imminent mass spin ispreferably smaller than a second threshold value corresponding to a massspin state, but can be otherwise defined. The threshold pressure ispreferably higher than the desired tire pressure, but can alternativelybe any other suitable pressure. In another example, the pressure sensorcan be configured to measure the pumping rate of a pump (e.g., primarypump 200, secondary pump 200 b, etc.), which can be indicative of aneccentric mass parameter (e.g., eccentric mass spin rate, etc.)indicating a mass spin state. Additionally and/or alternatively, thefluid pressure measurement can be used to analyze fluid purity (e.g.,blockages due to fluid particulates or contaminants could manifest as anincreased fluid pressure), or for any other suitable purpose. In aspecific example, the processing system 320 can detect an elevated fluidpressure based on a pressure measurement from the pressure sensor, andautomatically initiate a purge cycle and/or a regeneration cycle, wherecontaminated fluid can be purged, and purified pressurized fluid can bereintroduced into the pump system 15. However, the pressure sensor canbe configured in any suitable manner.

In a third variation, the sensor set 310 can include a vehicle sensorconfigured to collect vehicular sensor data (e.g., motion sensor data,camera data, proximity sensor data, on-board diagnostic system data,light sensor data, etc.) indicative of current and/or imminent eccentricmass spin. In an example, the processing system 320 can be configured totranslate vehicle movement (e.g., speed, acceleration, etc.) data to anindicator of imminent mass spin, and/or to an indicator of a mass spinstate. However, one or more vehicle sensors can be configured in anysuitable manner.

In a fourth variation, the sensor set 310 can include a vibration sensormounted to the monitored component (e.g., housing 30 of the pump system15, eccentric mass 140, motion transformer 120, etc.) and configured tomeasure vibration of the monitored component. In an example, theprocessing system 320 can be configured to determine that the eccentricmass 140 is in and/or approaching the mass spin state in response todetermining that the housing vibration measurements substantially matcha predetermined vibration pattern associated with the mass spin stateand/or imminent mass spin. However, the vibration sensor can beotherwise configured.

Sensors of the sensor set 310 can additionally or alternatively includeany one or more of: motion sensors, acoustic sensors, thermal sensors,electrical sensors, magnetic sensors, fluid sensors, navigation sensors,optical sensors, orientation sensors, inertial sensors (e.g.,accelerometers, gyroscopes, magnetometers, etc.), pressure sensors,proximity sensors, or any other suitable type of sensor. The sensors canoptionally be paired with a signal emitter (e.g., acoustic emitter,optical emitter, etc.) that emits a signal sensed by the respectivesensor.

However, the sensor set 310 can be configured in any suitable manner.

3.3.B Control System—Processing System

The control system 300 can include a processing system 320 thatfunctions to receive measurements of the eccentric mass parameter fromthe sensor set 310, determine that the eccentric mass 140 is in a massspin state and/or approaching a mass spin state based on themeasurements of the eccentric mass parameter, and/or operate astabilization mechanism 550 (e.g., fluid valve) in response todetermination that the eccentric mass 140 is in and/or approaching themass spin state.

The processing system 320 is preferably mounted to the housing 30 of thepump system 15 (e.g., to the housing interior, to the housing exterior),but can additionally or alternatively be mounted to the drive mechanism100, be external the tire inflation system 10, or be positioned at anyother suitable location.

The processing system 320 is preferably connected to and/or communicablycoupled (e.g., through a wired electrical connection, a wirelesscommunication link, etc.) to the stabilization mechanism 550 (e.g., toactuate the stabilization mechanism 550), the sensor set 310 (e.g., tocontrol the sensor set 310 to collect sensor data), the power module,and/or the communications module 350, but can be communicably coupledwith any suitable component.

The processing system 320 is preferably configured to receive andprocess one or more sensor set measurements for detecting mass spin(e.g., imminent mass spin, a mass spin state, etc.) and/or a non-spinstate. In a variation, the processing system 320 is configured to derivean eccentric mass 140 angular velocity from the sensor measurements, todetect imminent mass spin in response to determining an eccentric mass140 angular velocity in a first mass spin frequency range, to detect amass spin state in response to determining an eccentric mass 140 angularvelocity value in a second mass spin frequency range, and/or to detect anon-spin state in response to the angular velocity value outside ofand/or exiting a mass spin frequency range (e.g., the second mass spinfrequency range). In another variation, the processing system 320 can beconfigured to execute a predictive model with sensor set 310measurements and/or other features (e.g., environmental data, location,etc.) for determining a mass spin state and/or non-spin state.

The mass spin frequency range corresponding to a mass spin statepreferably includes the resonant frequency of the drive mechanism 100,but can be otherwise defined. Additionally or alternatively, the massspin frequency range corresponding to imminent mass spin can include theresonant frequency of the drive mechanism 100. A mass spin frequencyrange can include a lower frequency threshold (lower than the resonantfrequency of the drive mechanism 100 and a higher frequency threshold(greater than the resonant frequency of the drive mechanism 100. Thelower and higher frequency thresholds can be pre-determined (e.g.,pre-determined by the manufacturer), manually determined (e.g., by auser of the pump system 15), dynamically determined (e.g., determined bya machine learning module, based on observed behavior), or determined inany other suitable manner. The resonant frequency of the drive mechanism100 can be determined from the drive mechanism mass and the drivemechanism mechanical coupling (e.g., effective spring constant) to itsexternal environment (e.g., the housing 30 of the pump system 15), theeccentric mass' 140 mass and the eccentric mass' 140 mechanical couplingto the motion transformer 120, or otherwise determined. The resonantfrequency of the drive mechanism 100 can optionally be determined fromthe static unbalance (sometimes called force unbalance) of the drivemechanism 100 about the drive mechanism 100 center of mass and/ormechanical damping (e.g., viscosity) in the drive mechanism 100 couplingto the external environment.

The processing system 320 is preferably configured to selectivelycontrol one or more stabilization mechanisms 550 in response todetecting mass spin (e.g., detecting an imminent mass spin state and/orthat the eccentric mass is in a mass spin state). In a variation, theprocessing system 320 can be configured to control a valve actuator of afluid valve to transition the fluid valve into an open position (e.g.,in response to detecting an eccentric mass 140 angular velocity enteringa mass spin frequency range) and/or closed position (e.g., in responseto detecting an eccentric mass 140 angular velocity exiting a mass spinfrequency range). In other variations, the processing system 320 can beconfigured to electrically control engagement and/or disengagement ofdriving and driven members of a clutch mechanism, to actively control atransient coupling mechanism to separate and/or combine sections of acollectively formed eccentric mass 140, to actively control a masscouple 142 and/or mass transformer couple (e.g., to couple and/ordecouple mounted components), and/or to otherwise control one or morestabilization mechanisms 550.

The processing system 320 can be a central processing unit (CPU),microprocessor, GPU, organic processor, microchip, a remote server, orbe any other suitable processing system 320 configured to receive sensormeasurements, to perform a computation based in part on thosemeasurements, and/or to issue an executable operation based in part onthe output of the computation. While some variants of the processingsystem 320 include only a single processor, alternative variants caninclude two or more processors. In variants including multipleprocessors, the processors can be mounted in approximately the samelocation on the same component (e.g., two processors both mounted on thehousing 30, with one processor functioning as a primary processor and asecond processor functioning as a backup option in case of primaryprocessor malfunction) or in disparate locations (e.g., mounted todifferent components of the pump system 15). In variants includingmultiple processors, the multiple processors can work in combination(e.g., performing computations in parallel and then subsequentlysynthesizing outputs, performing computations in series with atroubleshoot check after each step, etc.), can work independently (e.g.,different processors separately perform computations and their outputsare compared in order to detect malfunction), or in any other suitablemanner. In one example, the processing system 320 is mounted to thehousing 30 and configured to receive measurements from one or moresensors. In this example, the processing system 320 can use thosemeasurements to monitor system performance (e.g., recording systemparameters for troubleshooting purposes, detecting a fluid blockage in acomponent of the pump system 15, determining that the eccentric mass 140is in a mass spin state, etc.) and can undertake an action.

However, the processing system 320 can be configured in any suitablemanner.

3.3.C Control System—Power Module

The control system 300 can include a power module, which functions toprovide power to power-consuming components (e.g., sensor set 310,processing module, communications module 350, etc.) of the tireinflation system 10.

The power module is preferably electrically connected to thepower-consuming components of the tire inflation system 10. The powermodule is preferably positioned proximal the processing system 320(e.g., mounted to the interior housing), but can be otherwise located.

The power module preferably includes a battery (e.g., a rechargeablebattery such as a lithium chemistry battery, non-rechargeable battery,etc.) but can additionally or alternatively include any combination ofsuitable energy storage, generation, and/or conversion modules. In anexample, the power module includes a rechargeable battery configured toharvest a portion of the rotational motion of the rotating surface 20,the primary pump 200, and/or other suitable component in order torecharge the battery. The rechargeable battery can be mounted to thehousing 30 and electrically connected to the processing system 320. Inthis example, the power module can include an electric generatorelectrically connected to the rechargeable battery. The electricgenerator can include a stator and a rotor, where the rotor can includesa portion of the motion transformer 120, the electric generatorconfigured to convert a portion of rotational energy (e.g., facilitatedby the motion transformer 120) into electrical potential energy.Additionally or alternatively, the electric generator can include anarmature rotationally coupled to the rotating surface 20 and/or theprimary pump 200, and configured to convert a portion of rotationalenergy into electric potential energy). However, the power module andcomponents of the power module can be otherwise configured.

3.3.D Control System—Communications Module

The control system 300 can include a communications module 350, whichfunctions to enable communication between the tire inflation system 10and a user. Additionally or alternatively, the communications module 350can function to enable communication between the processing system 320and the sensor set 310, the processing system 320 and one or morestabilization mechanism 550, and/or communications with a remote server.

The communications module 350 can be within or mounted to the housing 30of the primary pump 200 (e.g., interior housing), other components ofthe primary pump 200, the drive mechanism 100, and/or any other suitablecomponent.

The communications module 350 can include one or more: antennas, wiredcommunication modules (e.g., communication pins, Ethernet components,powerline components, etc.), wireless communication modules (e.g.,Bluetooth components such as Bluetooth Low Energy components, WiFichips, Zigbee, Z-wave, radios, radiofrequency, infrared, magneticinduction, etc.) and/or any other suitable components.

In a variation, the communications module 350 can be wirelessly coupled(e.g., via Bluetooth) to a user device. For example, the communicationsmodule 350 can be configured to communicatively connect the processingsystem 320 to a native application running on an external user device.In this variation, the communications module 350 can be configured totransmit mass spin state-related notifications (e.g., mass spin statestatus), driving prompts (e.g., prompting the user to decelerate),and/or other suitable communications to the user. Further, thecommunications module 350 can be configured to receive user instructionsand/or to transmit the user instructions to the processing module (e.g.,to actuate a stabilization mechanism 550, to initiate sensor datacollection, etc.).

In another variation, the communications module 350 can be electricallyconnected to the processing module and wirelessly coupled to thestabilization mechanism 550. In this variation, the communicationsmodule 350 can be configured to transmit instructions generated by theprocessing module to the stabilization mechanism 550 (e.g., foractuating the stabilization mechanism 550 into an alleviation modeand/or recovery mode.), which can include a stabilization mechanism 550communications module 350. In another variation, the communicationmodule can be wirelessly coupled to one or more sensors of the sensorset 310, and configured to wirelessly receive sensor measurements and totransmit the sensor measurements to the processing module (e.g., througha wired electrical connection). In this variation, sensors of the sensorset 310 can include a sensor communication module (e.g., antenna fortransceiving data).

However, the communications module 350 can be configured in any suitablemanner

3.4 Pump System—Housing

The pump system 15 can additionally or alternatively include a housing30 that functions to couple the pump system components to the rotatingsurface 20. The housing 30 is preferably configured to removablystatically couple to the rotating surface 20, but can otherwise coupleto the rotating surface 20. For example, the housing 30 can beconfigured to mount to a surface of a wheel. More preferably, thehousing 30 is configured to mount (e.g., via a set of bolts, screws,etc.) to the hub of a tire, but can alternatively mount to the rim,axle, or any other suitable component of a tire.

The housing 30 is preferably rotatably coupled to the drive mechanism100 and is preferably statically coupled to the pump body 240 of theprimary pump 200, such that the primary pump 200 rotates with thehousing 30. However, the housing 30 can be otherwise coupled to thepumping system components. The housing 30 can additionally function tomechanically protect the pump system components, where the housing 30preferably substantially encloses the pump system components. Thehousing 30 is preferably substantially rigid, but can alternatively besubstantially flexible. The housing 30 is preferably substantially fluidimpermeable, but can alternatively be permeable to fluid. In onevariation of the pump system 15, the housing 30 functions as the firstreservoir 400, where the primary pump 200 inlet is fluidly connected toand draws fluid from the housing interior. In this variation, thehousing 30 can include an inlet manifold fluidly connecting the housinginterior with the ambient environment. The inlet manifold preferablyincludes a water-selective membrane that preferentially permits gas flowtherethrough (e.g., the gas flow rate through the water-selectivemembrane is higher than the water flow rate through the water-selectivemembrane). The inlet manifold can alternatively include an inlet valvethat controls fluid flow into the housing interior, but canalternatively not include any valves. The inlet valve is preferably apassive one-way valve operable between an open mode in response to thehousing interior pressure falling below or being equal to the ambientpressure and a closed mode in response to the housing interior pressureexceeding the ambient pressure. However, the inlet valve can be anactive valve, a two-way valve, or any other suitable valve.

Additionally or alternatively, the housing 30 can be configured in anysuitable manner.

3.5 Relief Valve

As shown in FIG. 4, the pump system 15 can optionally include a reliefvalve 135 which functions to leak air from the interior of the secondreservoir 500 (e.g. tire interior) of the into the pump system 15, morepreferably into the housing 30 of the pump system 15 (e.g. the firstreservoir 400), but can alternatively leak air from the second reservoir500 to the ambient environment.

The relief valve 135 preferably connects to the second reservoirinterior through the Schrader valve of the second reservoir 500, but canotherwise fluidly connect to the second reservoir 500. The relief valve135 preferably operates between an open mode where air flow through therelief valve 135 is permitted, and a closed mode where air flow throughthe relief valve 135 is prevented. The relief valve 135 preferablyincludes an open threshold pressure, and is preferably a fail closedrelief valve 135. Alternatively, the relief valve can be a fail openvalve 135, or fail in any other suitable configuration. The shutoffthreshold is preferably set to leak second reservoir pressure at a ratesubstantially close to the flow rate of the pump (e.g. 10 cubicinches/minute), but can alternatively leak at a rate substantially closeto the normal second reservoir leakage rate (e.g., 1-3 psi per month),but can alternatively leak second reservoir pressure at a higher orlower rate. The relief valve 135 can be actively operated (e.g., by aprocessing system configured to control the relief valve 135 betweenopen and closed modes), passively operated, and/or otherwise controlled.

Additionally or alternatively, the relief valve 135 can be configured inany manner analogous to embodiments, variations, and examples describedin U.S. application Ser. No. 14/839,009 filed 28 Aug. 2015, which isherein incorporated in its entirety by this reference. However, therelief valve 135 can be otherwise configured.

4. Method

As shown in FIG. 9, a method 600 for stabilizing a tire inflation systemfor a tire supported by a wheel includes: actuating an actuating elementrelative a pump cavity using relative motion between a housing and aneccentric mass rotatably coupled to the housing at a rotation axis S610,measuring an eccentric mass parameter indicative of mass spin (e.g.,imminent mass spin, a mass spin state, etc.) with a sensor set S620,determining a mass spin state S630, and selectively controllingoperation of one or more stabilization mechanisms 550 S640. The method600 can additionally or alternatively include controlling thestabilization mechanism to operate in a recovery mode S650. The method600 functions to detect and/or mitigate eccentric mass spin resultingfrom conversion of rotary motion (e.g., of a tire) into a pumping forcethat facilitates eccentric mass angular rotation at a resonantfrequency.

4.1 Actuating an Actuating Element.

Block S610 recites: actuating an actuating element relative a pumpcavity using relative motion between a housing (e.g., statically mountedto the wheel) and an eccentric mass (e.g., having a center of massoffset from the rotation axis) rotatably coupled to the housing at arotation axis. Block S610 functions to convert rotary motion (e.g., of atire) into a pumping force. The actuating element is preferablyautomatically actuated concurrently with rotation of the rotatingsurface (e.g., while a user drives the vehicle), but can be actuatedwhen the rotating surface is stationary (e.g., in a variation where theprimary pump can rotate independently from the rotating surface such asby way of a roller bearing mass couple), and/or at any suitable time.

However, actuating an actuating element can be performed in any suitablemanner.

4.2 Measuring an Eccentric Mass Parameter.

Block S620 recites: measuring an eccentric mass parameter indicative ofmass spin with a sensor set, which functions to collect an eccentricmass parameter for determining a mass spin state in Block S630.

Measuring an eccentric mass parameter can be performed substantiallycontinuously, at predetermined time intervals (e.g., every second, every10 seconds, every minute, every half hour, etc.), in response tosatisfaction of a condition (e.g., detecting rotating surface motion,starting the vehicle engine, manual request from a user at a user devicecommunicably coupled to the communications module, etc.), and/or at anysuitable frequency. Measuring an eccentric mass parameter is preferablyperformed prior to detecting a mass spin state, but can additionally oralternatively be performed concurrently, in response to, and/or afterdetecting a mass spin state, and/or at any suitable time. In variationswhere the sensor set includes a plurality of sensors, eccentric massparameters can be measured at different sensors according to differentfrequencies and/or at different times.

However, measuring an eccentric mass parameter can be performed in anysuitable manner.

4.3 Determining a Mass Spin State.

Block S630 recites: determining a mass spin state. Block S630 functionsto identify when the eccentric mass is approaching a mass spin state(e.g., is in an imminent mass spin state) or is in a mass spin state.Determining a mass spin state and/or imminent mass spin is preferablybased on one or more eccentric mass parameters (e.g., measured in BlockS620), but can additionally or alternatively be based on environmentalconditions (e.g., weather conditions, road conditions, etc.), userbehavior (e.g., driver behavior, passenger behavior), vehicle conditions(e.g., tire conditions, engine conditions, etc.), and/or any othersuitable information indicative of a mass spin state. Block S630preferably includes actively determining a mass spin state and/orimminent mass spin (e.g., using a processing system and sensor set), butcan additionally or alternatively include passively determining the massspin state and/or imminent mass spin (e.g., mechanically, with a passivedetection system, etc.), and/or through any suitable mechanism actively(e.g., using a processing system and sensor set), or in any othersuitable manner.

In a first variation, the method boo can include measuring the angularvelocity of the a drive mechanism component (e.g., an eccentric mass)about a rotational axis, and determining that the eccentric mass is inand/or approaching the mass spin state based on determining that theangular velocity of the eccentric mass falls within a mass spin angularfrequency range defined by a lower angular frequency threshold and anupper angular frequency threshold encompassing a resonant frequency ofthe drive mechanism. For example, determining that the eccentric mass isapproaching a mass spin state (e.g., determining that the eccentric massis in an imminent mass spin state) include determining that an angularvelocity of the eccentric mass falls within a first mass spin angularfrequency range, and determining that the eccentric mass is in a massspin state can be based on determining that the angular velocity fallswithin a second mass spin angular frequency range. The upper angularfrequency threshold of the second mass spin angular frequency range ispreferably greater than the upper angular frequency threshold of thefirst mass spin angular frequency range. The first and second mass spinangular frequency ranges are preferably non-overlapping, but can beoverlapping (e.g., where the frequency ranges both encompass theresonant frequency of the drive mechanism), or otherwise defined.Alternatively, the eccentric mass can be determined to be approachingthe mass spin state (e.g., determined as being in the imminent mass spinstate) in response to the angular velocity falling within apredetermined range (e.g., of the angular frequency threshold),increasing beyond a threshold rate, or otherwise determined.

In a second variation, the method 600 can include measuring adisplacement amplitude of the eccentric mass 140 in a plane normal tothe rotational axis of the drive mechanism 100. For example, the method600 can include measuring the displacement amplitude with a displacementsensor (e.g., an accelerometer, gyroscope, IMU, etc.) mounted to themonitored component (e.g., mounted to the housing for monitoring thedisplacement amplitude of the housing), or alternatively mounted to asurface opposing the monitored component, or to any suitable element. Asthe drive mechanism 100 approaches a resonance condition, the system canbegin oscillating vertically relative to a gravity vector (e.g.,“bouncing” or “shaking”). As such, Block S630 can include determiningthat a time series of the measured displacement amplitude substantiallymatches a predetermined pattern associated with a mass spin state (e.g.,through machine learning approaches), a predetermined pattern associatedwith imminent mass spin, and/or a predetermined pattern associated witha non-spin state.

In a third variation, the method 600 can include measuring the timedependence of the eccentric mass oscillation amplitude. In a thirdvariation, the method 600 can include measuring, with a motion sensor(e.g., gyroscope mounted to the eccentric mass), oscillations of thedrive mechanism (e.g., eccentric mass). Drive mechanism oscillations canindicate that the motion is underdamped (e.g., oscillatory with anamplitude that decays exponentially in time with a decay constant),critically damped (e.g., relaxes towards equilibrium exponentiallywithout oscillating and with a decay constant equal to the resonantfrequency of the drive mechanism), or overdamped (e.g., relaxes towardsequilibrium exponentially without oscillating and with a decay constantthat is shorter in inverse time than the resonant frequency of the drivemechanism). Block S630 can include generating a comparison between adrive mechanism oscillation pattern (e.g., derived from measured drivemechanism oscillations) and one or more predetermined oscillationpatterns associated with an underdamped state, critically damped state,or overdamped state. Further, Block S630 can include determining a massspin state and/or imminent mass spin in response to the comparisonindicating an underdamped state (e.g., based on a high similarity scorebetween the drive mechanism oscillation pattern and a predeterminedpattern associated with an underdamped state, a mass spin state, and/orimminent mass spin).

In a fourth variation, the method boo can include monitoring therelative timing of the vertical oscillations of the eccentric mass tothe vertical oscillations of the drive mechanism overall. As the drivemechanism approaches a resonance condition, the drive mechanism and theeccentric mass can both begin to oscillate in a plane normal to therotational axis of the drive mechanism (e.g., vertically relative to agravity vector) about their respective equilibrium positions. Theresonance condition can be a phase relationship, where he stabilizationmechanism can determine that the eccentric mass is in the mass spinstate or determine that the eccentric mass is approaching the mass spinstate (e.g., determine that the eccentric mass is in the imminent massspin state) when the oscillations of the eccentric mass and theoscillations of the drive mechanism are out of phase (or are close tobeing out of phase) by a phase angle of approximately 90° (e.g., thedrive mechanism is moving upwards about its vertical equilibriumposition at the approximately same time that the eccentric mass 140 isat its maximal vertical displacement) (e.g., where the phase differenceis between 80°-100°, etc.). However, any other suitable resonancecondition can be additionally or alternatively used. Alternatively, thestabilization mechanism (or any other suitable component of the pumpsystem) can determine that the eccentric mass can be in and/orapproaching a mass spin state in any suitable manner.

Determining an eccentric mass state is preferably in real-time (e.g., asthe processing system receives sensor set measurements indicating aneccentric mass spins state), but can additionally or alternatively be innon-real time (e.g., processing sensor set measurements at predeterminedtime intervals, in response to threshold conditions, etc.), and/or atany suitable time.

However, determining a mass spin state and/or imminent mass spin can beperformed in any suitable manner.

4.4 Selectively Controlling Operation of a Stabilization Mechanism.

Block S640 recites: selectively controlling operation of one or morestabilization mechanisms (e.g., to operate in alleviation mode). BlockS640 functions to compensate for forces applied by the primary pump onthe driving mechanism (e.g., a motion transformer of the drivingmechanism). For example, Block S640 can include selectively venting thepump cavity by controlling a stabilization mechanism fluid valve (e.g.,by applying an electric current with a processing system to a valveactuator), fluidly connecting the pump cavity to a fluid reservoir, tooperate in an open position.

Selectively controlling a stabilization mechanism is preferably inresponse to detecting the mass spin state, but can additionally oralternatively be in response to detecting an unstable state of the motortransformer, the motor transformer couple, the mass couple, and/or anyother suitable component.

Blocks S640 and S630 are preferably performed by a processing system,but can additionally or alternatively be performed with any suitablecomponent (e.g., user device, vehicle).

However, selecting controlling operation of a stabilization mechanismcan be performed in any suitable manner.

4.5 Controlling the Stabilization Mechanism to Operate in a RecoveryMode.

The method 600 can optionally include Block S650, which recites:controlling the stabilization mechanism to operate in a recovery mode.Block S650 functions to return the pump system 15 to normal operationfor converting rotary motion into a pumping force for inflating a tire.In one example, this can include shutting off the stabilizationmechanism fluid valve. However, normal pumping system operation can beotherwise achieved.

Controlling the stabilization mechanism to operate in a recovery mode ispreferably in response to determining that the eccentric mass has exitedthe mass spin state and/or the imminent mass spin state. Determining amass spin state exit is preferably based on eccentric mass parametersmeasured by a sensor set after determining a mass spin state (e.g. inBlock S640). For example, the method 600 can include measuring one ormore post-spin state eccentric mass parameters after detecting a massspin state, and detecting a mass spin state exit by processing thepost-spin state eccentric mass parameters with the processing system.However, determining a mass spin state exit can be performed at anysuitable time.

In a first variation, the method 600 can include measuring the angularvelocity of the drive mechanism component about a rotational axis afterdetecting a mass spin state, and determining a mass spin state exit inresponse to determining that the angular velocity falls outside the massspin angular frequency range. In a second variation, the method boo caninclude measuring eccentric mass displacement amplitude after detectinga mass spin state, and determining a mass spin state exit in response toa time series of the displacement amplitude matching a predeterminedprofile associated with a non-spin state. In an third variation, themethod boo can include measuring the time dependence of the eccentricmass oscillation amplitude after detecting a mass spin state, anddetermining a mass spin state exit based on the drive mechanismoscillation pattern matching a predetermined pattern associated with acritically damped and/or overdamped state. In a fourth variation, themethod 600 can include monitoring the relative timing of verticaloscillations of the eccentric mass and the drive mechanism overall, anddetermining a mass spin state exit based on the relative timingindicating a phase angle associated with a non-spin state.

However, controlling the stabilization mechanism to operate in arecovery mode can be performed in any suitable manner.

Although omitted for conciseness, the preferred embodiments includeevery combination and permutation of the various system components andthe various method processes, where the method processes can beperformed in any suitable order, sequentially or concurrently.

As a person skilled in the art will recognize from the previous detaileddescription and from the figures and claims, modifications and changescan be made to the embodiments of the invention without departing fromthe scope of this invention defined in the following claims.

We claim:
 1. A tire pressure management system for a tire supported by awheel, the system comprising: a pump comprising a pump chamber; ahousing mounted to the pump, the housing configured to mount the pump toa hub of the wheel; a tire inflation manifold configured to fluidlyconnect the pump chamber to the tire; a valve, connected between thepump chamber and a fluid sink, wherein the valve is separate from thetire inflation manifold; and a control system configured to selectivelyactuate the valve based on a parameter of the pump.
 2. The system ofclaim 1, further comprising a drive mechanism connected to the pump, thedrive mechanism configured to drive actuation of the pump, wherein theparameter of the pump comprises a back force applied by the pump on thedrive mechanism, wherein the control system is configured to selectivelyopen the valve in response to the back force exceeding a thresholdvalue.
 3. The system of claim 1, further comprising an eccentric massrotatably mounted to the housing and offset from a housing rotationalaxis, wherein the eccentric mass is configured to drive actuation of thepump, wherein the parameter of the pump comprises a parameter of theeccentric mass.
 4. The system of claim 3, further comprising a sensor,mounted to the housing and configured to monitor the parameter of thehanging mass.
 5. The system of claim 3, wherein the parameter of theeccentric mass comprises a rotational frequency of the eccentric mass,wherein the control system is configured to open the valve when therotational frequency falls within a predetermined range associated withan eccentric mass spin state, wherein the predetermined rangeencompasses a resonant frequency of the eccentric mass.
 6. The system ofclaim 1, further comprising: a battery mounted to the housing andelectrically connected to the valve; and a generator mounted to thehousing and electrically connected to the battery.
 7. The system ofclaim 6, wherein the generator comprises a stator statically mounted tothe housing, a rotor rotatably mounted to the housing, and a hangingmass statically mounted to the rotor, the hanging mass freely rotatablerelative to the housing.
 8. The system of claim 1, wherein the fluidsink comprises an ambient environment, wherein the valve selectivelyfluidly connects the pump chamber to the ambient environment.
 9. Thesystem of claim 1, wherein the tire inflation manifold comprises asecond valve configured to selectively fluidly connect the pump chamberto the tire.
 10. The system of claim 1, wherein the control systemcomprises a processor mounted to the housing and electrically connectedto the valve.
 11. A tire pressure management system for a tire supportedby a wheel, the system comprising: a housing configured to mount to asurface of the wheel; a pump mounted to the housing, the pump comprisingan actuation mechanism and a pump chamber; a drive mechanism actuatablyconnected to the actuation mechanism; a tire inflation manifoldconfigured to fluidly connect the pump chamber to the tire; and a valve,separate from the tire inflation manifold, that selectively fluidlyconnects the pump chamber to an ambient environment, wherein the valveis configured to actuate between an open and closed position based on aparameter of the pump.
 12. The system of claim 11, wherein the parameterof the pump comprises a back force applied by the pump on the drivemechanism, wherein the valve is configured to open when the back forceexceeds a predetermined force threshold.
 13. The system of claim 11,wherein the drive mechanism comprises an eccentric mass offset from ahousing center of rotation, the eccentric mass freely rotatable relativeto the housing.
 14. The system of claim 13, further comprising a sensorset configured to monitor a rotational frequency of the eccentric mass,wherein the valve is configured to open when the rotational frequencyfalls within a predetermined frequency range, wherein the predeterminedfrequency range encompasses a resonant frequency of the eccentric mass.15. The system of claim 11, wherein the drive mechanism comprises aneccentric mass, freely rotatable relative to the housing and offset froma housing rotational axis, wherein the valve comprises a centrifugalvalve tuned to open at a cracking rotational frequency, wherein thecracking rotational frequency is determined based on a resonantfrequency of the eccentric mass.
 16. The system of claim 11, wherein thevalve comprises an active valve, the system further comprising a controlsystem operably connected to the active valve and mounted to thehousing.
 17. The system of claim 16, wherein the active valve comprisesa solenoid, wherein the control system comprises a processing systemmounted to the housing.
 18. The system of claim 16, further comprising:an electric generator mounted to the housing; and a battery mounted tothe housing and electrically connected to the electric generator and theactive valve.
 19. The system of claim 18, wherein the electric generatoris driven by a hanging mass rotatably mounted to the housing.
 20. Thesystem of claim 11, further comprising a secondary pump fluidlyconnected to an inlet of the pump, wherein the secondary pump isactuatably connected to the drive mechanism.